Fluid flow control device

ABSTRACT

A flow controller adapted to control a flow of fluid within the flow controller, the flow controller having a flow path adapted to convey said fluid, wherein the cross-sectional area of the flow path varies along the flow path and wherein in at least a portion of its length the flow controller comprises an active surface capable of influencing the fluid flow through the flow path to cause vortical motion of the fluid within the fluid pathway.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation and claims the priority benefit ofPatent Cooperation Treaty application number PCT/AU2004/000862 filedJun. 29, 2004, which claims the priority benefit of Australian patentapplication number 2003903386 filed Jul. 2, 2003. The disclosure ofthese commonly owned applications is incorporated herein by reference.This application is also related to U.S. patent application Ser. No.10/882,412 filed Jun. 30, 2004.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to nozzles, diffusers and venturis. It maybe applied in any application in which conventional nozzles, diffusersand venturis are used.

2. Description of the Related Art

Nozzles, diffusers and venturis are specific types of ducts used inrelation to the flow of fluid. For the purpose of this specification, anozzle is intended to mean a duct of varying cross-sectional area whichis designed so that fluid flow is accelerated by a pressuredifferentiated between the inlet and the outlet. A diffuser is intendedto mean a duct of varying cross-sectional area which is designed so thatfluid flow is decelerated by an increase of pressure between the inletand the outlet. A venturi can be seen as a duct comprising a nozzlesection and diffuser section abutted in tandem.

Nozzles are widely used in the field of fluid flow as a means to providean accelerated stream of fluid and have many applications. Diffusers areused to decelerate fluid flow and again have many applications. Venturisare used to cause a short region of accelerated flow in a duct. It is awell known law of thermodynamics that the accelerated fluid flow isaccompanied by a reduced pressure, and that many applications ofventuris are directed to utilising the reduced pressure.

While nozzles, diffusers and venturis are widely used, it is also wellknown that their performance is affected considerably by turbulence andfrictional losses. These factors significantly limit the uses to whichsuch devices can be applied.

SUMMARY OF THE INVENTION

Accordingly, an exemplary embodiment of the present invention provides aflow controller adapted to control a flow of fluid within thecontroller, the flow controller having a flow path adapted to conveysaid fluid, wherein the cross-sectional area of the flow path variesalong the flow path and wherein in at least a portion of its length theflow controller comprises an active surface capable of influencing thefluid flow through the flow path.

According to an exemplary embodiment of the invention, the activesurface is adapted to cause rotational motion of fluid within the fluidpathway about the axis of flow of the fluid.

According to an exemplary embodiment of the invention, the activesurface is adapted to cause vortical motion of fluid within the fluidpathway about the axis of flow of the fluid.

According to an exemplary embodiment of the invention, the configurationof the active surface conforms to at least one logarithmic curveconforming to the Golden Section.

According to an exemplary embodiment of the invention the curvature ofthe active surface is uni-dimensional.

According to an exemplary embodiment of the invention the curvature ofthe active surface is bi-dimensional.

According to an exemplary embodiment of the invention, the curvature ofthe active surface varies in accordance with the Golden Section.

According to an exemplary embodiment of the invention, the curvature ofthe active surface conforms to an equiangular spiral.

According to an exemplary embodiment of the invention the curvature ofthe active surface is transverse to the central axis of the fluidpathway.

According to an exemplary embodiment of the invention the curvature ofthe active surface can be in a direction parallel to the central axis.

According to an exemplary embodiment of the invention the curvature ofthe active surface is both transverse to the central axis and isparallel to the direction of the central axis to define athree-dimensional surface conforming substantially or in the greaterpart to the Golden Section.

According to an exemplary embodiment of the invention, the fluid pathwayhas a spiral configuration. According to a preferred embodiment theconfiguration takes the form of a logarithmic helix or a volute or awhorl.

According to an exemplary embodiment of the invention, thecross-sectional area of the flow path varies logarithmicallysubstantially or in greater part in conformity to the Golden Section.

According to an exemplary embodiment of the invention, thecross-sectional area of the flow path varies to cause the incrementalvolume of the flow path to vary logarithmically.

According to an exemplary embodiment of the invention, the incrementalvolume is caused to vary in conformity with the Golden Ratio.

According to an exemplary embodiment of the invention, the activesurface has the configuration conforming to the external configurationof a shell of the phylum Mollusca, class Gastropoda or Cephalopoda.According to exemplary forms of the invention the active surfaceconforms to the external configuration of shells selected from thegenera Volutidea, Argonauta, Nautilus, Conidea or Turbinidea.

According to an exemplary embodiment of the invention, the activesurface has the configuration of the interior of shells of the phylumMollusca; classes Gastropoda or Cephalopoda. In particular embodiments,the active surface has the configuration of the interior of shellsselected from the genera Volutidea, Conidea, Turbinidea, Argonauta, orNautilus.

According to an exemplary embodiment of the invention, the configurationof the flow controller promotes substantially radially laminar fluidflow.

According to an exemplary embodiment of the invention, the flowcontroller comprises a nozzle.

According to an exemplary embodiment of the invention, the flowcontroller comprises a diffuser.

According to an exemplary embodiment of the invention, the flowcontroller comprises a venturi.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a chart of the Golden Section or Fibonacci Progression;

FIG. 2 is an isometric view of a nozzle according to a first embodiment;

FIG. 3 is an isometric view of a nozzle according to a secondembodiment;

FIG. 4 is an isometric view of a nozzle according to a third embodiment;

FIG. 5 is an isometric view of a diffuser according to a fourthembodiment;

FIG. 6 is a sectional elevation of a conventional venturi tube;

FIG. 7 is an isometric view of a venturi according to a fifthembodiment;

FIG. 8 is an isometric view of a venturi according to a sixthembodiment.

DETAILED DESCRIPTION

An embodiment of the invention is directed to a flow controller, thestructure of which is configured to cause the rate of a fluid flow to bealtered during passage through the controller. Each of the embodimentsis directed to a flow controller adapted to alter the rate of flow of afluid.

It has been found that all fluids when moving under the influence of thenatural forces of Nature, tend to move in spirals or vortices. Thesespirals or vortices generally comply to a mathematical progression knownas the Golden Ratio or a Fibonacci-like Progression.

Each of the embodiments serves, in the greater part, to enable fluids tomove in their naturally preferred way, thereby reducing inefficienciescreated through turbulence and friction which are normally found inapparatus commonly used for propagating fluid flow. Previously developedtechnologies have generally been less compliant with natural fluid flowtendencies.

The greater percentage of the surfaces of the flow controller of each ofthe embodiments described herein are generally designed in the greaterpart, in accordance with the Golden Section or Ratio or are designed toensure the volume of fluid flowing through the flow controller expandsor contracts in the greater part in accordance with the Golden Sectionand therefore it is a characteristic of each of the embodiments that theflow controller provides a fluid pathway which is of a spirallingconfiguration and which conforms at least in greater part to thecharacteristics of the Golden Section or Ratio.

The characteristics of the Golden Section are illustrated in FIG. 1which illustrates the unfolding of the spiral curve according to theGolden Section or Ratio. As the spiral unfolds the order of growth ofthe radius of the curve which is measured at equiangular radii (e.g., E,F, G, H, I and J) is constant. This can be illustrated from thetriangular representation of each radius between each sequence whichcorresponds to the formula of a:b=b:a+b which conforms to the ratio of1:0.618 approximately and which is consistent throughout the curve.

It is a characteristic of each of the embodiments that the curvature ofthe surfaces which form the flow controller takes a two dimensional orthree dimensional shape equivalent to the lines of vorticity or streaklines found in a naturally occurring vortex. In general, the curvatureof the surfaces substantially or in the greater part conform to thecharacteristics of the Golden Section or Ratio and that any variation incross-sectional area of the flow controller also substantially or ingreater part conforms to the characteristics of the Golden Section orRatio. In at least some of the embodiments, the curvature of the activesurface conforms to an equiangular spiral. Furthermore it has been foundthat the characteristics of the Golden Section or Ratio are found innature in the form of the external and internal configurations of shellsof the phylum Mollusca, classes Gastropoda and Cephalopoda and it is acommon characteristic of at least some of the embodiments that the fluidpathway defined by the flow controller corresponds generally to theexternal or internal configuration of shells of one or more of thegenera of the phylum Mollusca, classes Gastropoda and Cephalopoda.

It has been found that it is a characteristic of fluid flow that, whenit is caused to undergo a fluid flow through a pathway having acurvature substantially or in greater part conforming to that of theGolden Section or Ratio that the fluid flow over the surfaces issubstantially non-turbulent and as a result has a decreased tendency tocavitate. As a result, fluid flow over the surface is more efficientthan has been encountered in previous instances where the pathway doesnot substantially or in greater part correspond to that of the GoldenSection. As a result of the reduced degree of turbulence which isinduced in the fluid in its passageway through such a pathway, the flowcontrollers according to the various embodiments can be used forconducting fluid with a greater efficiency than has previously beenpossible with conventional flow controllers of equivalent dimensionalcharacteristics.

To assist the reader's understanding of the embodiments, the outersurfaces of the embodiments in the drawings are depicted in a waywhereby they would correspond with the inner surfaces, such as would bethe case if the walls of the embodiments are of constant thickness. Inthis way some concept of the helical/spiral configurations of the innersurfaces is conveyed. In practical fluid flow control devices, theconfiguration of the outer surface is not of significance to theembodiments and thus the outer surface could be configured as a simplesurface such as a cone, leaving the inner surface complex as suggestedin these drawings.

The first embodiment takes the form of a nozzle as shown in FIG. 2. Thenozzle 11 has a nozzle body 21, an outlet 22 and an inlet 23 which isadapted to be joined to a duct (not shown) such as a pipe, hose orsimilar providing a source of fluid under pressure. The nozzle body 21has an internal surface 25 which reduces in cross-sectional area to theoutlet 22. In addition, the internal surface of the nozzle may be seento twist in a combination helical manner and spiralling manner betweenthe input and the output. As indicated above, this twist is in aconfiguration which provides an active surface which conforms at leastin greater part to the characteristics of the Golden Section or Ratio.It will be seen that as a result of the twist, fluid flowing in thenozzle is caused to be given a rotational motion about the longitudinalaxis of the nozzle to thereby induce vortical motion in the fluid.

As a result of the vortical motion, the turbulence and friction in thenozzle are reduced considerably from that observed in a conventionalnozzle having a simple conical internal surface.

A second embodiment takes the form of a nozzle as shown in FIG. 3. Thesecond embodiment is of substantially similar construction to that ofthe first embodiment, and therefore in the drawings like parts aredenoted with like numerals. The second embodiment differs from the firstonly in the particular design of the nozzle in that it is relativelylonger and has greater twist. By varying the parameters of the nozzle,the formation of the vortical flow emitted from the nozzle outlet can becontrolled. In certain applications, it will be desirable for the outletto comprise a narrow vortical stream while in others, a diverging streamwill be required to promote mixing of the output with the surroundingfluid.

A third embodiment takes the form of a nozzle as shown in FIG. 4. Inthis embodiment, the twist in the flow surfaces causes the direction offlow to be diverted transversely to that of the incoming flow stream.This redirection is achieved without significant loss because theinternal surface of the nozzle is still configured to conform at leastin greater part to the characteristics of the Golden Section or Ratio.As a result, turbulence is substantially avoided.

It will be appreciated that a whole class of embodiments are possiblewhereby the output flow is directed obliquely relative to the directionof the input flow stream.

A fourth embodiment takes the form of a diffuser as shown in FIG. 5. Itmay be appreciated that a diffuser may comprise a flow controllersubstantially identical to a nozzle but with direction of flow reversed.In this regard, the diffuser of FIG. 5 corresponds with the nozzle ofFIG. 2 but having an internal surface 25 which increases incross-sectional area to the outlet 22. Therefore, in the drawings likenumerals are again used to depict like features. As with the nozzle,while the diffuser of FIG. 4 will induce vortical motion in the fluidflow, the precise characteristics of the output flow can be controlledby varying the design properties of the diffuser while maintaining theinner surface to conform at least in greater part to the characteristicsof the Golden Section or Ratio.

It has been previously been noted that the cross-sectional area of theprevious embodiments varies between the inlets to the outlets; for thenozzles, the area decreasing and for the diffusers, the area increasing.In a further development of the previous embodiments, it has been foundadvantageous, at least in certain circumstances to vary the incrementalvolume of the controller along the fluid pathway in a manner thatconforms to the characteristics of the Golden Section or Ratio. To takeadvantage of this aspect, further embodiments of the fluid flow controldevices as previously described are configured to conform with thisconstraint. As a result, the volume of fluid flowing through the flowcontroller expands or contracts in the greater part in accordance withthe Golden Ratio.

A fifth embodiment takes the form of a modified venturi tube as shown inFIG. 7. The modified venturi tube is best appreciated by comparison witha conventional venturi tube which is depicted In FIG. 6. In theconventional venturi tube of FIG. 6, a venturi 51 comprises an inlet 52,an outlet 53 and a constricted region 54. The constricted region 54comprises an entry 55, an exit 56 and a region of maximum constriction57. In the drawings, the flow is represented by flow lines 58.

When fluid is caused to flow into the inlet 52 of venturi 21, it isaffected by the entry 55 wherein the diameter of the fluid pathway isprogressively reduced until the region of maximum constriction 57 isreached. This constriction within the fluid pathway causes the speed atwhich the fluid is travelling to be increased. In accordance with wellknown laws of thermodynamics, this increase in fluid speed isaccompanied by a reduction in pressure of the fluid. Subsequent to theregion of maximum constriction 57, the fluid flow is affected by theexit 56 wherein the diameter of the fluid pathway is progressivelyincreased to the outlet 53. In the exit 56, the fluid is progressivelyslowed.

It is known that the energy losses at a venturi are very significant. Asmentioned above, these losses are caused both by friction andturbulence. In particular, it is well known that while the performanceof a venturi can be increased by increasing the ratio of the inletdiameter relative to the diameter of maximum constriction 57, it is alsoknown that in practice that any gains achieved by so reducing the regionof maximum constriction are rapidly cancelled by the increased losseswhich result.

As can be seen in FIG. 7, the modified venturi 61 comprises an inlet 62,an outlet 63, a region of maximum constriction 64, an entry 65 and anexit 66. It will be readily perceived that these portions conformgenerally to corresponding portions of the conventional venturi tube ofFIG. 6. In contrast however, the entry 64 and exit 65 are specificallydesigned to induce the fluid to move in accordance with the laws ofNature. As mentioned previously, the flow controller is designed with apathway having a curvature substantially or in greater part conformingto that of the Golden Section or Ratio. The fluid is thereby inducedinto vortical flow the greater part of which conforms to the GoldenSection or Ratio. The energy losses caused as a result of this vorticalflow are considerably lower than those which result from a conventionalventuri.

As a result of the considerably reduced energy losses caused by themodified venturi of the fifth embodiment, the apparatus may be used moreeffectively than previously has been possible. Firstly, it is possibleto increase the ratio of the area of inlet relative to the area ofmaximum constriction. This increases the relative pressure differencethat may be generated between the inlet and the region of maximumconstriction. This broadens the scope of use of the device.

A sixth embodiment takes the form of a modified venturi tube as shown inFIG. 8. The sixth embodiment, although somewhat different in appearance,operates in substantially the same manner as that of fifth embodimentand so, in the drawings, like parts are denoted with like numerals. Thesixth embodiment again comprises a duct, the area of cross-section ofwhich reduces from an inlet to a portion of maximum constriction, andthen increase to the outlet. The difference between the sixth embodimentand the fifth is that in the fifth embodiment the flow induces a vortexwhich has an axis of rotation which is co-linearly aligned with thecentral axis of the inlet, whereas in the sixth embodiment, the axis ofrotation of the vortex is disposed substantially transversely to thecentral the axis of the inlet.

It has been noted previously that in the embodiments of the modifiedventuri tube, the cross-sectional area of the duct varies along the flowpath, decreasing in the entry and increasing in the exit. As in theexamples of the nozzles and diffusers, it has been found advantageous,at least in certain circumstances to vary the incremental volume of thecontroller along the fluid pathway in a manner that conforms to thecharacteristics of the Golden Section or Ratio. To take advantage ofthis aspect, further embodiments of the modified venturi tubes aspreviously described are configured to conform with this constraint. Asa result, the volume of fluid flowing through the entry and exit of theventuri contracts or expands in the greater part in accordance with theGolden Ratio.

It has been found that, in at least certain configurations of theembodiments, the arrangements promote substantially radial laminar flowand it is believed that this assists the efficiency of the fluid flowwithin those arrangements

It should be appreciated that the scope of the present invention neednot be limited to the particular scope of the embodiments describedabove.

Throughout the specification, unless the context requires otherwise, theword “comprise” or variations such as “comprises” or “comprising”, willbe understood to imply the inclusion of a stated integer or group ofintegers but not the exclusion of any other integer or group ofintegers.

1. A method for altering a flow of fluid, the method comprising:receiving fluid from a fluid source, receipt of the fluid occurring at afluid flow control apparatus; inducing the fluid received from the fluidsource to have a rotational motion about an axis via a flow path of thefluid flow control apparatus, the flow path situated between an inletand an outlet of the fluid flow control apparatus, the flow pathincluding a cross-sectional area that progressively decreases from theinlet to a region of maximum constriction and progressively increasesfrom the region of maximum constriction to the outlet, wherein thecross-sectional area includes both a region of increasing diameter and aregion of decreasing diameter between the inlet and the region ofmaximum constriction and further includes both a region of increasingdiameter and a region of decreasing diameter between the region ofmaximum constriction and the outlet; and expelling from the fluid flowcontrol apparatus the fluid received from the fluid source, the expelledfluid including a vortical motion resulting from the induced rotationabout the axis, and wherein a pressure differentiation is induced in thefluid between the receipt and expulsion of the fluid, thedifferentiation induced while the fluid traverses the fluid flow controlapparatus.
 2. The method of claim 1, further including accelerating theflow of fluid as a result of the pressure differentiation inducedbetween the receipt and expulsion of the fluid.
 3. The method of claim1, further including decelerating the flow of fluid as a result of thepressure differentiation induced between the receipt and expulsion ofthe fluid.
 4. The method of claim 1, further including accelerating anddecelerating the flow of fluid as a result of the pressuredifferentiation induced between the receipt and expulsion of the fluid.5. A fluid flow control apparatus for altering a flow of fluid, thefluid flow control apparatus comprising: an inlet configured to receivefluid from a fluid source; an outlet configured to expel the fluidreceived from the fluid source; and a flow path situated between theinlet and the outlet and within a body of the fluid flow controllerapparatus, the flow path including a cross-sectional area thatprogressively decreases from the inlet to a region of maximumconstriction and progressively increases from the region of maximumconstriction to the outlet, wherein the cross-sectional area includesboth a region of increasing diameter and a region of decreasing diameterbetween the inlet and the region of maximum constriction and furtherincludes both a region of increasing diameter and a region of decreasingdiameter between the region of maximum constriction and the outlet, thecross-sectional area varying along the length of the flow path therebyinducing pressure differentiation within the body of the fluid flowcontrol apparatus, the flow path configured to convey the fluid from theinlet to the outlet and wherein at least a portion of the length of thebody includes an internal surface area configured to induce a rotationalmotion about an axis as the fluid traverses the flow path therebyresulting in a vortical motion in the fluid as the fluid is expelledfrom the outlet.
 6. The fluid flow control apparatus of claim 5, whereinat least a portion of the internal surface area substantially conformsto a logarithmic curve, wherein the radius of the logarithmic curvemeasured at equiangular radii unfolds at a constant order of growth. 7.The fluid flow control apparatus of claim 5, wherein a portion of thecross-sectional area of the flow path varies logarithmically and theradius of the logarithmic variation measured at equiangular radiiunfolds at a constant order of growth.
 8. The fluid flow controlapparatus of claim 5, wherein the cross-sectional area of the flow pathcauses a logarithmic variance in the incremental volume of the flowpath.
 9. The fluid flow control apparatus of claim 5, wherein theinternal surface area substantially conforms to the external or interiorconfiguration of a shell of the phylum Mollusca.
 10. The fluid flowcontrol apparatus of claim 5, wherein the internal surface areasubstantially conforms to the external or interior configuration of ashell of the genera Volutidea.
 11. The fluid flow control apparatus ofclaim 5, wherein the vortical motion in the fluid expelled from theoutlet is further substantially radially laminar.
 12. The fluid flowcontrol apparatus of claim 5, wherein the inlet is configured to receivea pressurized fluid source.
 13. The fluid flow control apparatus ofclaim 5, wherein the vortical motion of the fluid expelled from theoutlet reduces turbulence in the flow of fluid.
 14. The fluid flowcontrol apparatus of claim 5, wherein the vortical motion of the fluidexpelled from the outlet reduces friction in the flow of fluid.
 15. Thefluid flow control apparatus of claim 5, wherein the outlet isconfigured to generate a diverging vortical stream.
 16. The fluid flowcontrol apparatus of claim 5, wherein the flow path is transverselydiverted with respect to the received fluid.
 17. The fluid flow controlapparatus of claim 5, wherein the internal surface area substantiallyconforms to the external or interior configuration of a shell of theclass Gastropoda.
 18. The fluid flow control apparatus of claim 5,wherein the internal surface area substantially conforms to the externalor interior configuration of a shell of the class Cephalopoda.
 19. Thefluid flow apparatus of claim 5, wherein the internal surface areasubstantially conforms to the external or interior configuration of ashell of the genera Argonauta.
 20. The fluid flow apparatus of claim 5,wherein the internal surface area substantially conforms to the externalor interior configuration of a shell of the genera Nautilus.
 21. Thefluid flow apparatus of claim 5, wherein the internal surface areasubstantially conforms to the external or interior configuration of ashell of the genera Conidea.
 22. The fluid flow apparatus of claim 5,wherein the internal surface area substantially conforms to the externalor interior configuration of a shell of the genera Turbinidea.
 23. Thefluid flow control apparatus of claim 5, wherein the variance in thecross-sectional area includes an increase along the length of the flowpath from the inlet to the outlet.
 24. The fluid flow control apparatusof claim 5, wherein the flow path is configured in a spiral.
 25. Thefluid flow control apparatus of claim 24, wherein the spiral is alogarithmic helix.
 26. The fluid flow control apparatus of claim 24,wherein the spiral is a volute.
 27. The fluid flow control apparatus ofclaim 24, wherein the spiral is a whorl.